US11867269B2 - Shift group for power shift transmission - Google Patents
Shift group for power shift transmission Download PDFInfo
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- US11867269B2 US11867269B2 US17/065,682 US202017065682A US11867269B2 US 11867269 B2 US11867269 B2 US 11867269B2 US 202017065682 A US202017065682 A US 202017065682A US 11867269 B2 US11867269 B2 US 11867269B2
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 130
- 230000008878 coupling Effects 0.000 claims abstract description 59
- 238000010168 coupling process Methods 0.000 claims abstract description 59
- 238000005859 coupling reaction Methods 0.000 claims abstract description 59
- 239000000969 carrier Substances 0.000 claims description 11
- 230000009365 direct transmission Effects 0.000 claims description 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 239000011159 matrix material Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
Definitions
- the present disclosure relates to a shift group for a power shift transmission having a summation unit which comprises a planetary stage and a branching coupling assigned to the planetary stage, wherein the summation unit is designed such that a mechanical power may be transmitted to a second shaft in a first shifting state of the branching coupling via a first or a second power path and in a second shifting state of the branching coupling both via the first and via the second power path.
- Power shift transmissions are used in agricultural machines and serve for transmitting a mechanical power from a drive motor to a drive train.
- the transmissions are designed such that they permit a high gear ratio spread, and at the same time have a low mass inertia to be synchronized.
- Such transmissions generally have a plurality of gears in order to be able to cover the high gear ratio spread.
- These individual gears are implemented by shifting individual shift groups relative to one another, wherein a first shift group is generally denoted as a gear shift group and a second shift group is denoted as a range shift group.
- Each of these shift groups has a specific number of shiftable gears, wherein the total number of gears is produced by multiplying the gears from both shift groups.
- shift groups of the type described above are known from the prior art, wherein for the person skilled in the art it is always desired, on the one hand, to increase the number of gears so that it is possible to configure the transitions relative to the transmission ratios between the individual gears to be as smooth as possible within the gear ratio spread and, on the other hand, to reduce the number of components and structural units required therefor. This not only leads to a cost saving. Due to the smaller number of components, the required constructional space for the power shift transmission may also be significantly reduced. Due to the smaller number of components, the susceptibility to error or the maintenance effort are also reduced.
- individually shiftable transmission units which differ from one another relative to their transmission ratio are provided, respectively one thereof in the first power path and two thereof in the second path.
- the ratio of the transmission units in the second power path to the first power path is 2:1.
- the transmission units are individually shiftable via one respective power path, so that in the case of three transmission units a total of three different gears are formed. By combining in each case two transmission units in one respective power path, two further possible gears are produced, so that five gears are able to be produced with a total of three transmission units. Since each of the transmission units is individually shiftable via one respectively assigned coupling, the shift group in such an embodiment has a total of four couplings in addition to the branching coupling. In contrast to an embodiment in the form of a conventional spur gear group, therefore, by combining two power paths one coupling may be dispensed with.
- the term “summation unit” within the scope of the present disclosure means a combination of a planetary stage and a branching coupling, by which it is possible to divide the power flowing into the shift group into two power paths.
- This is possible by planetary stages generally having three inputs or outputs which may be combined together and which may be individually connected to shafts.
- a conventional embodiment consists of a combination of a sun gear, a plurality of planetary gears which circulate around the sun gear and which are connected together via a common planet carrier, and a ring gear which in turn adjoins the planet carrier.
- the summation unit in this case may be already arranged on the power input or even on the power output.
- the power may be divided via one of the planetary stages and combined together again via the other planetary stage, wherein in each case one of the planetary stages is connected to the first shaft and the respective other planetary stage is connected to the second shaft.
- the first shaft may be connected to the at least one transmission unit which is configured as a planetary stage and the second shaft may be connected to the summation unit.
- the second shaft may be connected to the at least one transmission unit which is configured as a planetary stage and the first shaft may be connected to the summation unit.
- planetary stages generally consist of a combination of a sun gear, a planet carrier and a ring gear. If at least one of the transmission units is configured as a planetary stage an embodiment has also proved particularly advantageous, however, in which two planet carriers arranged coaxially to one another are provided, wherein the planets of the first planet carrier are in engagement with the planets of the second planet carrier and wherein the planet carriers are coupled together.
- This is a planetary stage in which two groups of planets are arranged in succession in the radial direction, whereby a reversal of the rotational direction may be produced in a simple manner. For example, it is possible that not all of the transmission units produce a rotational direction of the second shaft in the same rotational direction. Instead, a reversal of the rotational direction may be obtained, for example, by one of the transmission units, whereby reverse gears are also possible by a direct connection.
- the summation unit comprises two planetary units which are arranged adjacent to one another and which in each case comprise a sun gear and a planet carrier circulating around the sun gear, wherein the planetary units differ from one another regarding the transmission ratio thereof and the planet carriers are connected together.
- Such an embodiment is particularly expedient when the summation unit is arranged on the power input, wherein in a first shifting state the planet carrier is directly connected to the first shaft and the second shaft is connected to one of the sun gears.
- all of the transmission units within the scope of the present disclosure may be configured as a planetary stage.
- at least one of the transmission units is configured as a spur gear stage in the first or second power path. Therefore, this spur gear stage has two spur gear sets with in each case a drive gear and an output gear, wherein the output gear of the first spur gear set is connected via an auxiliary shaft to the drive gear of the second spur gear set.
- Both spur gear sets in each case have a specific transmission ratio, wherein the total transmission ratio of the spur gear stage is produced by multiplying the transmission ratio of the first and second spur gear set.
- At least one of the transmission units is configured as a direct transmission in the first or in the second power path.
- each transmission unit comprises one respective transmission coupling or is configured as a transmission coupling.
- a multiplate clutch is suitable, in particular, as a type of coupling since this multiplate may be actuated even at different rotational speeds of the elements to be coupled together, and produces a synchronization of the rotational speeds by a frictional connection.
- the transmission units in the first and in the second power path when connected individually and thus not combined together, may produce a rotation of the shaft in a first rotational direction.
- individual transmission units may produce an opposing rotation in a second rotational direction.
- the shift group has three forward gears and two reverse gears. To this end, two variants have proved particularly advantageous.
- all of the transmission units are configured in the first and the second power path such that in the first shifting state of the branching coupling they produce a rotation of the second shaft in a first rotational direction, wherein the power paths may be combined together in the second shifting state such that the second shaft has a rotation in a second rotational direction which opposes the first rotational direction.
- a reverse operation is only possible by combining the two power paths. This may be brought about, for example, via a planetary stage with a ring gear, wherein in such a case the summation unit forms the planetary stage which combines the two power paths.
- At least two transmission units are configured in the second power path such that in the first shifting state of the branching coupling the transmission units produce an opposing rotational direction of the second shaft.
- at least one gear provided for reverse travel may be directly shifted, wherein the transmission ratios of the individual transmission units are configured such that even when combining the two power paths together, an additional forward and an additional reverse gear are configured so that a total of three forward and two reverse gears are also provided here.
- the number of transmission units may also be increased. Particularly, however, exactly one more transmission unit is always arranged in the second power path compared to the first power path.
- a further subject of the present disclosure is a transmission, in particular a power shift transmission with a shift group according to the present disclosure, wherein the summation unit is arranged in the power flow upstream or downstream of the transmission units.
- the transmission has at least one further shift group which is arranged upstream or downstream of the shift group according to the present disclosure.
- a further subject of the present disclosure is a method for shifting the shift group, wherein the branching coupling for a first shifting state is closed and one of the transmission units from the first and the second power path is connected and wherein the branching coupling for a second shifting state is opened and in each case one of the transmission units from the first and the second power path is connected.
- FIG. 1 shows the shift group according to a first embodiment
- FIG. 2 shows the shift group according to FIG. 1 in a power flow diagram
- FIG. 3 shows a shift matrix for a shift group according to FIG. 1 .
- FIG. 4 shows a shift group according to a second variant
- FIG. 5 shows a shift group according to a third variant
- FIG. 6 shows a power flow diagram for the shift groups according to FIGS. 4 and 5 .
- FIG. 7 shows a shift matrix for the shift groups according to FIGS. 4 and 6 .
- FIG. 1 shows the shift group according to the present disclosure according to a first variant.
- the power is introduced via a first shaft 10 into the shift group and transmitted via the shift group to a second shaft 20 .
- the shift group has a summation unit 40 which consists of a planetary stage 41 and a branching coupling 45 .
- the summation unit 40 is arranged at the end in the power flow and directly adjoins the second shaft 20 .
- the planetary stage 41 of the summation unit 40 has a sun gear 42 , a planet carrier 43 , with a plurality of planets circulating around the sun gear, and a ring gear 44 which is directly connected to the second shaft 20 .
- a transmission unit 50 which is also configured as a planetary stage and which similar to the summation unit 40 has a sun gear 52 , a planet carrier 53 and a ring gear 54 , adjoins the first shaft 10 .
- the planet carrier 53 is directly connected to the first shaft 10 .
- the ring gear 54 may be blocked relative to a housing 51 via a transmission coupling 55 which is configured as a ring gear brake.
- the power is branched via the transmission unit 50 to a first and a second power path I, II, wherein the summation unit 40 combines the two power paths I, II again and transmits the power to the second shaft 20 .
- Only one transmission unit 60 which is configured as a spur gear set is provided in the first power path I.
- This transmission unit 60 directly adjoins the first shaft 10 via the planet carrier of a third transmission unit 70 and the planet carrier 53 of the first transmission unit 50 and is driven irrespective of the position of the individual transmission couplings 55 , 65 , 75 , provided the first shaft 10 is set in rotation.
- the spur gear stage consists of two individual spur gear sets 61 , 62 , the rotation being transmitted thereby to the transmission coupling 65 .
- This transmission coupling in turn directly adjoins the planet carrier 43 of the summation unit 40 .
- a further shifting state may be achieved by the transmission coupling 55 being closed instead of the transmission couplings 65 , 75 , whereby the ring gear 54 is blocked relative to the housing 51 .
- Both the transmission unit 50 and the transmission unit 70 in this case are arranged in the second power path II and thus in an open state of the branching coupling 45 may be combined with the transmission unit 60 which is configured as a spur gear set.
- FIG. 2 shows how power may be transmitted from the first shaft 10 to the second shaft 20 , wherein the transmission couplings 55 , 75 or the transmission units 50 , 70 are arranged in a second power path II and the spur gear sets 61 , 62 or the transmission coupling 65 are arranged in the first power path I.
- the branching coupling 45 is opened, the two power paths I, II may be combined together in the planetary stage 41 .
- the branching coupling 45 is closed, only one transmission unit 50 , 60 , 70 may be used in each case from one of the two power paths I, II in order to transmit the power to the second shaft 20 .
- the summation unit 40 is arranged with the planetary stage 41 and the branching coupling 45 in the power flow downstream of the transmission units 50 , 60 70 .
- FIG. 3 shows a shift matrix of the shift group according to FIGS. 1 and 2 .
- a total of three forward gears V 1 , V 2 , V 3 and two reverse gears R 1 , R 2 are provided, the forward gears being formed by individual shifting of the individual transmission couplings 55 , 65 , 75 , so that the branching coupling 45 and one respective transmission coupling 55 , 65 , 75 are closed.
- the transmission coupling 65 is closed, then the transmission coupling 75 is closed and only then is the transmission coupling 55 closed.
- the reverse gears R 1 , R 2 are obtained by combining the power paths I, II together, wherein the transmission unit 60 is combined with one of the transmission units 50 , 70 .
- the branching coupling 45 is opened and the transmission coupling 65 and one of the transmission couplings 55 , 75 are closed.
- FIG. 4 shows the shift group according to the present disclosure according to a second variant, in which in contrast to the version shown in FIG. 1 the summation unit 40 is now arranged on the power input and thus directly adjoins the first shaft 10 .
- the inner planet carrier of the planetary gear coupling 45 is directly connected to the sun gear 42 of the planetary stage 41 and the outer planet carrier is directly connected to the planet carrier 43 of the planetary stage 41 , so that accordingly the two power paths I, II may be formed via the sun gear 42 and the planet carrier 43 .
- the arrangement of the summation unit 40 in the power input is shown, in particular, very clearly by comparing the view with FIG. 6 , wherein from the structural perspective, the planetary stage 41 is arranged between the transmission unit 50 and the transmission unit 80 .
- the transmission unit 70 is also configured here as a direct gear.
- the transmission units 50 , 80 are both designed as planetary stages.
- the transmission unit 50 has a sun gear 52 , a planet carrier 53 and a ring gear 54 , wherein the ring gear 54 may be fixed relative to the housing 51 via a transmission coupling 55 which is configured as a ring gear brake.
- the planet carrier 53 is also directly connected to the inner planet carrier of the branching coupling 45 and thus at the same time also directly to the planet carrier 43 of the planetary stage 41 .
- the transmission unit 80 also has a sun gear 81 and a ring gear 83 which is able to be fixed relative to the housing 51 in a similar manner to the transmission unit 50 by a transmission coupling 85 which is configured as a ring gear brake.
- the transmission unit 80 has two planet carriers 82 which are arranged coaxially to one another and connected together.
- the planet carriers are directly connected to the sun gear 52 of the transmission unit 50 .
- the transmission unit 80 in an individually connected shifting state forms a reverse gear or produces a reversal of the rotational direction of the second shaft 20 .
- This second shaft 20 is directly connected to the planet carrier 82 .
- a coupling to the sun gear 81 may be implemented by coupling-in the transmission coupling 75 of the transmission unit 70 .
- FIG. 6 illustrates once again which transmission units 50 , 70 , 80 are arranged in the power paths I, II. Accordingly, the transmission unit 50 is arranged in the first power path I and the transmission units 70 , 80 are arranged in the second power path II.
- This power flow diagram also similarly applies to a third variant according to FIG. 5 .
- this summation unit 40 differs substantially by the specific design of the summation unit 40 .
- this summation unit now has two planetary stages 41 which are arranged adjacent to one another and which in each case have a sun gear 42 a , 42 b and a planet carrier 43 a , 43 b .
- the two planet carriers 43 a , 43 b are directly connected together and to the outer planet carrier of the branching coupling 45 , which in turn adjoins the first shaft 10 .
- a rotation of the first shaft 10 produces a rotation of the planet carrier 43 a , 43 b .
- the first sun gear 42 a also adjoins the inner planet carrier of the summation unit 40 so that when coupled-in the sun gear 42 a also has the same rotational speed as the first shaft 10 .
- the power outputs of the summation unit 40 are formed via the first sun gear 42 a and via the second sun gear 42 b , wherein these power outputs are designed in a similar manner to the variant according to FIG. 4 .
- FIG. 7 shows the shift matrix for the shift groups according to FIGS. 4 to 6 . Accordingly, two forward gears V 2 , V 3 may now be directly achieved by connecting the branching coupling 45 and the planetary gear couplings 75 , 55 . Additionally, a directly shiftable reverse gear R 1 is available by connecting the transmission coupling 85 .
- a further forward gear V 1 and a further reverse gear R 2 may be obtained, wherein the branching coupling 45 is opened.
- the forward gear V 1 is shifted and by combining the transmission units 70 , 50 the reverse gear R 2 is shifted.
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Abstract
Description
Claims (16)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102019216299.1 | 2019-10-23 | ||
DE102019216299.1A DE102019216299A1 (en) | 2019-10-23 | 2019-10-23 | Shift group for powershift transmission |
Publications (2)
Publication Number | Publication Date |
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US20210123513A1 US20210123513A1 (en) | 2021-04-29 |
US11867269B2 true US11867269B2 (en) | 2024-01-09 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US17/065,682 Active 2041-06-11 US11867269B2 (en) | 2019-10-23 | 2020-10-08 | Shift group for power shift transmission |
Country Status (3)
Country | Link |
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US (1) | US11867269B2 (en) |
EP (1) | EP3812618A1 (en) |
DE (1) | DE102019216299A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102020121209A1 (en) | 2020-08-12 | 2022-02-17 | Deere & Company | powershift transmission and vehicle |
US12044296B2 (en) | 2021-12-20 | 2024-07-23 | Deere & Company | Power shift transmission |
Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3545304A (en) | 1969-05-01 | 1970-12-08 | Gen Motors Corp | Angle input power transmission |
US6575866B2 (en) * | 2001-04-09 | 2003-06-10 | New Venture Gear, Inc. | Hybrid drive system for motor vehicle with powershift transmission |
DE10260179A1 (en) | 2002-12-20 | 2004-07-01 | Zf Friedrichshafen Ag | Multi-speed gearbox for road vehicle has divided load path with odd-numbered gears in first path and even-numbered gears in second path and has double input clutch and additional clutch at output |
EP1367296B1 (en) | 2001-03-05 | 2011-12-07 | Aisin Aw Co., Ltd. | Transmission for vehicle |
WO2013159995A1 (en) * | 2012-04-27 | 2013-10-31 | Zf Friedrichshafen Ag | Multi-stage power-shift transmission |
US8596157B2 (en) | 2010-08-25 | 2013-12-03 | Deere & Company | Powershift transmission with twenty-four forward modes |
EP3109509A1 (en) | 2015-06-25 | 2016-12-28 | Deere & Company | Gearbox assembly |
US9879761B2 (en) | 2014-10-30 | 2018-01-30 | Deere & Company | Powershift transmission with twenty-seven forward modes |
US10086686B2 (en) | 2016-01-14 | 2018-10-02 | Deere & Company | Transmission with a mode selection apparatus |
US10352401B2 (en) | 2015-05-04 | 2019-07-16 | Deere & Company | Transmission arrangement |
US10539207B2 (en) | 2015-05-04 | 2020-01-21 | Deere & Company | Transmission arrangement |
EP3770465A1 (en) | 2019-07-22 | 2021-01-27 | Deere & Company | Transmission |
US11187310B2 (en) | 2019-10-23 | 2021-11-30 | Deere & Company | Gear mechanism, use of a gear mechanism and method for a gear mechanism |
US11313445B2 (en) | 2019-10-23 | 2022-04-26 | Deere & Company | Transmission |
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2019
- 2019-10-23 DE DE102019216299.1A patent/DE102019216299A1/en active Pending
-
2020
- 2020-09-24 EP EP20198073.7A patent/EP3812618A1/en not_active Withdrawn
- 2020-10-08 US US17/065,682 patent/US11867269B2/en active Active
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3545304A (en) | 1969-05-01 | 1970-12-08 | Gen Motors Corp | Angle input power transmission |
EP1367296B1 (en) | 2001-03-05 | 2011-12-07 | Aisin Aw Co., Ltd. | Transmission for vehicle |
US6575866B2 (en) * | 2001-04-09 | 2003-06-10 | New Venture Gear, Inc. | Hybrid drive system for motor vehicle with powershift transmission |
DE10260179A1 (en) | 2002-12-20 | 2004-07-01 | Zf Friedrichshafen Ag | Multi-speed gearbox for road vehicle has divided load path with odd-numbered gears in first path and even-numbered gears in second path and has double input clutch and additional clutch at output |
US8596157B2 (en) | 2010-08-25 | 2013-12-03 | Deere & Company | Powershift transmission with twenty-four forward modes |
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Also Published As
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US20210123513A1 (en) | 2021-04-29 |
EP3812618A1 (en) | 2021-04-28 |
DE102019216299A1 (en) | 2021-04-29 |
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